US4172688A - Device for anti-rolling signalling for cable laying tractors - Google Patents

Device for anti-rolling signalling for cable laying tractors Download PDF

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Publication number
US4172688A
US4172688A US05/848,861 US84886177A US4172688A US 4172688 A US4172688 A US 4172688A US 84886177 A US84886177 A US 84886177A US 4172688 A US4172688 A US 4172688A
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United States
Prior art keywords
load
force
pipe
laying
lever arm
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Expired - Lifetime
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US05/848,861
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English (en)
Inventor
Carlo Cecchi
Roberto D. Pescarmona
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Fiat Allis Europe SpA
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Fiat Allis Macchine Movimento Terra SpA
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/88—Safety gear
    • B66C23/90—Devices for indicating or limiting lifting moment

Definitions

  • This invention relates in general to signalling apparatus, and in particular, to a signalling device for indicating maximum applied operational loading conditions.
  • this invention relates to a signalling device for indicating an applied loading condition as a percentage of a maximum operational loading condition which is especially suitable for use in pipe-laying machinery to directly relate the operational forces applied to a pipe-laying boom regardless of the lateral position of the boom relative to the pipe layer.
  • a lifting crane including a lifting boom is articulated about a pivot axis carried by the tractor frame.
  • a cable connected hook or other suitable connector is used to hold and lift a pipe coupled about the upright end of the boom through a pulley arrangement which allows the hook-connected pipe to be raised or lowered in response to the operation of a winch carried by the tractor.
  • a second cable is connected to the upright end of the boom and passes about an idler pulley to a second winch carried by the tractor frame so that the boom may be pivoted about the pivot axis to effect lateral movement of the pipe.
  • various signalling devices have been developed to alert the machine operator to conditions which indicate approach to a potentially dangerous situation.
  • these devices signal the operator the possibility of the pipe layer overturning during various operational conditions whenever a critical or overturning load is reached.
  • Some such devices compare the tension in the cable coupling the pipe to the tractor frame with a predetermined referenced value which represents a percentage of the critical rolling load corresponding to each lateral position of the side boom arm. When the reference load or tension is reached, an alarm is sounded to indicate the approach of the critical rolling load.
  • Another type of signalling device for pipe layers employs a coincidence type device which detects the position of the side arm or boom and compares the boom position with a value for the critical rolling load corresponding to every such position.
  • This device is excessively complex in its application to the system, and requires that the particular load being lifted by the pipe layer be determined. This determination is extremely inconvenient in field operation due to variations in the load from materials which may accumulate in the pipe and which may vary during movement of the pipe while it is being placed into a trench.
  • Another object of this invention is to improve signalling devices for pipe-laying machinery.
  • a further object of this invention is to allow the operator of pipe-laying equipment to control the operative loading conditions of the pipe layer in response to the approach of a critical loading condition.
  • a signalling device operatively coupled between the side arm or lifting boom of a pipe layer and the frame thereof in a predetermined fixed position such that movement of the signalling device relative to the fixed position, which occurs in response to the operational load, is directly related to the critical or rolling load for any lateral position of the side arm or lifting boom.
  • FIG. 1 is a front profile view of a mechanical schematic representation of a pipe layer of the crawler tractor type provided with a representation of the anti-rolling signalling device according to this invention
  • FIG. 3 is a sectional view of the apparatus disclosed in FIG. 2 taken along lines 3--3;
  • FIG. 4 is a perspective view of a portion of the anti-rolling signalling device to better illustrate the components thereof;
  • FIG. 5 is an exploded view of the anti-rolling signalling device shown in FIG. 4 to better illustrate the details thereof;
  • FIG. 7 is a front profile view of a mechanical schematic representation of a crawler tractor pipe layer showing the use of the anti-rolling signalling device with a hydraulic boom connection between the upright end of the side arm or lifting boom and the tractor frame.
  • a pipe layer 1 of the crawler tractor type comprising a tractor body and frame 2 supported by a pair of endless tracks 3 and 4.
  • the boom arm 6 has at its opposite upper or free end a frame 8 carrying a group of pulleys 9 utilized to effect raising and lowering of the pipe 10.
  • a cable 11 is secured at one end to a tractor supported winch 11a and passes about the pulleys 9 and a second group of pulleys 9a which support, through a hook 10a, the cable secured pipe 10. Operation of the winch 11a controls raising and lowering of the pipe 10 through the interconnected pulleys 9 and 9a.
  • a second cable 13, utilized to move the boom arm 6 about the pivot axis 7, extends from a tractor supported winch 13a into operative connection with a group of pulleys 12 carried by the boom frame 8 and a group of return pulleys 14 which are supported by the tractor and are utilized in the anti-rolling signalling device 100. Operation of the winch 13a controls lifting and lowering of the boom arm 6 about the pivot axis 7 to effect lateral movement of the pipe 10.
  • the return pulleys 14 are rotatable about an axis of rotation 15 and are carried upon a pivotal crank structure 16.
  • the crank structure 16 is pivotal about an axis of rotation 17 which is parallel both to the pulley axis 15 of the return pulleys 14 and the pivot axis 7 of the lifting boom 6. While the distance between the axes 15 and 17 is greatly enlarged in FIGS. 1, 6 and 7 to better illustrate the principles of operation of the anti-roll signalling device 100, in actuality the distance between these axes is much smaller as shown in the actual embodiment illustrated in FIGS. 2-5. Referring to FIGS.
  • the return pulleys 14 are rotatably supported about a pivot pin 19 on bearings 18 such that the axis of the pivot pin 19 coincides with the axis of rotation 15 of the return pulleys.
  • the crank structure 16 includes two shaft portions 20 extending outwardly on both sides of the pivot pin 19 with their center line offset in an eccentric position therewith.
  • the shafts 20 are rotatably supported in the tractor frame 2 by means of support bearings 21 such that the axis of rotation of the support shafts 20 forms an oscillation or pivot axis 17 of the crank structure 16.
  • a linkage rod 34 At the end 23a of the torsion bar 23, which is fixed to one of the shafts 20 and, therefore, free to turn in bearings 21 twisting about its common axis 17, there is fixed one end of a linkage rod 34.
  • An opposite end of the linkage rod 34 is pivotally connected about a pivot pin 35 to a pivot strut 26 which is in turn connected by a pin 27 to a U-shaped plate 28 rigidly fixed to the pin 27.
  • the U-shaped plate 28 is carried within a box 31 on a pivot pin 29 both of which are fixedly secured on the tractor frame 2.
  • a small flat indicator plate 30, shaped like a circular sector and having a radially extending edge 33, is rigidly secured to the U-shaped plate 28 for rotational movement therewith.
  • the circular sector shaped plate 30 is also positioned within the box 31 which is closed by a lid 31a having an opening or aperture 32 formed therein.
  • An angular scale with progressive numbers increasing up to a maximum of 100 is inscribed about the periphery of the opening 32 in the lid 31 a.
  • the radial edge 33 of the circular sector plate 30 is positioned adjacent to the aperture 32 and functions as an index from which a machine operator may read the graded scale as the edge 33 moves relative thereto.
  • the force transmitted to the side boom 6 when lifting a pipe 10 is indicated by P and the resultant force which cable 13 transmits to the axis of rotation 15 of the return pulleys 14 is indicated by T.
  • the force T is directed along the line which joins the axes of the group of pulleys 12 and 14, which is not precisely exact but, in engineering practice is considered acceptable.
  • the offset distance between the center line 17 of the crank structure 16 and the center line 15 of the return pulleys 14 is greatly exaggerated for convenience of illustration and identified by reference K.
  • Force T is such as to balance the force exerted on the lift boom 6 by the normal operational load force P such that the moment exerted about the pivot axis 7 of the boom arm 6 by force P and by force T are substantially equal.
  • Force T is also the force which acts on the group of return pulleys 14 to effect pivoting of the axis of rotation 15 of the pulleys about the center line 17 of the crank structure 16.
  • the torsion bar 23 Since the torsion bar 23 is fixed to the tractor frame 2 at one end, pivoting of the axis of rotation 15 of the pulleys 14 about the center line 17 of the crank structure 16 will twist the torsion bar 23 through an angle F which is proportional both to the resultant force T and the distance K, between the center line 15 of the return pulleys 14 and the center line 17 of the crank structure 16.
  • the distance K illustrated in FIG. 6 is substantially increased from the actual distance between the center lines 15 and 17 as illustrated in FIGS. 2 and 3.
  • Distance H represents the distance between the pivot axis 7 of the boom 6 and the effective application of the resultant force T applied to the return pulleys 14.
  • Rolling of the pipe layer occurs when the crawler tractor 1 is rotated about a longitudinal axis which extends close to the outside edge of the track supporting roller on the lower part of the endless track and indicated in FIG. 6 as point A.
  • the endless track becomes separated from the track rollers behaving therefore as if it were free in respect to the latter.
  • the turning moment arm about the longitudinally extending axis A is constant as it depends only on the characteristic dimensions of the tractor.
  • the critical or overturning moment occurs as the pivot axis 7 of the lifting boom 6 is approaching or lies in a plane extending parallel to the tractor support surface and passing through the rolling axis A and is, due to the relatively close proximity of pivot 7 and axis A, approximately equal to the moment exerted by a critical rolling load P about the pivot axis 7.
  • the moment exerted by a critical load P about the pivot axis 7 of the lifting boom 6 can be determined independently of determining the angular position of the lift boom 6 relative to the tractor 1. Since the forces exerted on the lift boom 6 must balance, this moment, prior to rolling, must be equal to the moment exerted by the resultant forces T about the pivot axis 7.
  • the resultant force T therefore, in the rolling or critical conditions, is inversely proportional to the distance H. Because this distance varies with the position of the boom arm 6, similarly the magnitude of the resultant force T at rolling conditions will vary. In the example illustrated, the value of the resultant force T varies about 10-15%.
  • the amount of twist to the torsion bar 23 is represented by F, the angle of rotation of the crank structure 16 about its axis of rotation 17, and is proportional to the product of the resultant force T and the distance of its application (K) from the pivot axis 17.
  • F degree of rotation
  • pivot or oscillation axis 17 and the axis of rotation 15 of the pulleys 14 should lie in a common plane inclining downward with respect to the tractor support plane as to form an angle B of approximately 55%, but an angle between 30° and 70° is suitable.
  • the edge 33 of the plate 30 is rotated through an angle corresponding to the twist in the torsion bar 23. Therefore, for any degree of rotation of the plate 30 there is indicated a percentage between the moment applied to the tractor from the operative load P and the critical rolling load regardless of the pivotal or lateral position of the boom arm 6. Since such angular movement will be indicated both during static and dynamic loading conditions the anti-rolling signalling device 100 allows the machine operator to observe all such loading conditions and achieve a much more effective operation of the pipe layer.
  • the pipe layer illustrated differs from that described with reference to FIGS. 1-6 only in the control of the lifting boom 6.
  • the lifting boom 6 is controlled by a hydraulic actuator 40 instead of the pulley system previously described.
  • the hydraulic actuator as is well known, is pivoted at one end 41 to the side boom frame 8 and is connected at its opposite end 42, in the exaggerated manner as shown in FIG. 1, to the crank structure 16 as previously described. All remaining details of the pipe layer illustrated in FIG. 7 are identical to those of the pipe layer illustrated in FIGS. 1-6 and are indicated as the same numbers.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Jib Cranes (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Agricultural Machines (AREA)
US05/848,861 1976-11-26 1977-11-07 Device for anti-rolling signalling for cable laying tractors Expired - Lifetime US4172688A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT69825A/76 1976-11-26
IT69825/76A IT1072049B (it) 1976-11-26 1976-11-26 Apparecchiatura citofonica bicanalae a conversazione simultanea a viva voce

Publications (1)

Publication Number Publication Date
US4172688A true US4172688A (en) 1979-10-30

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Family Applications (1)

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US05/848,861 Expired - Lifetime US4172688A (en) 1976-11-26 1977-11-07 Device for anti-rolling signalling for cable laying tractors

Country Status (7)

Country Link
US (1) US4172688A (OSRAM)
JP (1) JPS5369410A (OSRAM)
BR (1) BR7707793A (OSRAM)
CA (1) CA1060848A (OSRAM)
DE (1) DE2752504A1 (OSRAM)
GB (1) GB1596055A (OSRAM)
IT (1) IT1072049B (OSRAM)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4575305A (en) * 1983-11-18 1986-03-11 Bon Ton Rolle Limited Truck mounted tube bundle pulling apparatus
US4666365A (en) * 1983-11-18 1987-05-19 Bon Ton Rolle Limited Tube bundle pulling apparatus
US5409346A (en) * 1991-10-31 1995-04-25 Grether; Martin Self-loading and unloading forklift truck
USRE36884E (en) * 1988-12-19 2000-09-26 Cytec Technology Corp. Mannich acrylamide polymers
US20040190995A1 (en) * 2003-03-24 2004-09-30 Komatsu Ltd. Pipelayer
US8726529B2 (en) 2012-03-27 2014-05-20 Cnh Industrial America Llc Rotary sensor assembly
US20190337776A1 (en) * 2018-05-07 2019-11-07 Caterpillar Inc. Pipelayer machine having hoisting system with pivotable fairlead
US20190352148A1 (en) * 2018-05-21 2019-11-21 Caterpillar Inc. Machine having hoisting system with instrumented fairlead
US10988353B1 (en) 2019-11-07 2021-04-27 Michael S. Kelly Power winch equipment crane with hinge members
US11259453B2 (en) 2019-11-07 2022-03-01 Michael S. Kelly Power winch equipment crane

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IE862081L (en) * 1986-08-01 1988-02-01 Geard Bourke Determining the weight of a load in a loading bucket of a¹loading machine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB389929A (en) * 1931-12-17 1933-03-30 Arthur Mort Improvements in or relating to cranes and like lifting devices
US2022844A (en) * 1934-11-03 1935-12-03 Herbert A Christian Indicator
US2983140A (en) * 1956-10-01 1961-05-09 Martin Decker Corp Load indicating and anchoring device for cables and other lines
US3187913A (en) * 1963-04-30 1965-06-08 Hough Co Frank Implement position control mechanism
US4042116A (en) * 1975-01-24 1977-08-16 Fiat-Allis Construction Machinery, Inc. Track laying tractor with movable boom which can be tilted laterally
US4112750A (en) * 1975-08-12 1978-09-12 Nippon Hoist Co., Ltd. Hook device

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB389929A (en) * 1931-12-17 1933-03-30 Arthur Mort Improvements in or relating to cranes and like lifting devices
US2022844A (en) * 1934-11-03 1935-12-03 Herbert A Christian Indicator
US2983140A (en) * 1956-10-01 1961-05-09 Martin Decker Corp Load indicating and anchoring device for cables and other lines
US3187913A (en) * 1963-04-30 1965-06-08 Hough Co Frank Implement position control mechanism
US4042116A (en) * 1975-01-24 1977-08-16 Fiat-Allis Construction Machinery, Inc. Track laying tractor with movable boom which can be tilted laterally
US4112750A (en) * 1975-08-12 1978-09-12 Nippon Hoist Co., Ltd. Hook device

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4575305A (en) * 1983-11-18 1986-03-11 Bon Ton Rolle Limited Truck mounted tube bundle pulling apparatus
US4666365A (en) * 1983-11-18 1987-05-19 Bon Ton Rolle Limited Tube bundle pulling apparatus
USRE36884E (en) * 1988-12-19 2000-09-26 Cytec Technology Corp. Mannich acrylamide polymers
US5409346A (en) * 1991-10-31 1995-04-25 Grether; Martin Self-loading and unloading forklift truck
US20040190995A1 (en) * 2003-03-24 2004-09-30 Komatsu Ltd. Pipelayer
US6893189B2 (en) * 2003-03-24 2005-05-17 Komatsu Ltd. Pipelayer
US8726529B2 (en) 2012-03-27 2014-05-20 Cnh Industrial America Llc Rotary sensor assembly
US20190337776A1 (en) * 2018-05-07 2019-11-07 Caterpillar Inc. Pipelayer machine having hoisting system with pivotable fairlead
US10807839B2 (en) * 2018-05-07 2020-10-20 Caterpillar Inc. Pipelayer machine having hoisting system with pivotable fairlead
US20190352148A1 (en) * 2018-05-21 2019-11-21 Caterpillar Inc. Machine having hoisting system with instrumented fairlead
US10773934B2 (en) * 2018-05-21 2020-09-15 Caterpillar Inc. Machine having hoisting system with instrumented fairlead
US10988353B1 (en) 2019-11-07 2021-04-27 Michael S. Kelly Power winch equipment crane with hinge members
US11259453B2 (en) 2019-11-07 2022-03-01 Michael S. Kelly Power winch equipment crane

Also Published As

Publication number Publication date
JPS5369410A (en) 1978-06-20
DE2752504A1 (de) 1978-06-01
BR7707793A (pt) 1978-06-13
JPS5627742B2 (OSRAM) 1981-06-26
GB1596055A (en) 1981-08-19
IT1072049B (it) 1985-04-10
CA1060848A (en) 1979-08-21

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